EP0766788A1 - Moteur a pistons radiaux hydrostatique reglable - Google Patents

Moteur a pistons radiaux hydrostatique reglable

Info

Publication number
EP0766788A1
EP0766788A1 EP96902897A EP96902897A EP0766788A1 EP 0766788 A1 EP0766788 A1 EP 0766788A1 EP 96902897 A EP96902897 A EP 96902897A EP 96902897 A EP96902897 A EP 96902897A EP 0766788 A1 EP0766788 A1 EP 0766788A1
Authority
EP
European Patent Office
Prior art keywords
cam ring
eccentricity
radial piston
measuring device
piston machine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP96902897A
Other languages
German (de)
English (en)
Other versions
EP0766788B1 (fr
Inventor
Volkmar Leutner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0766788A1 publication Critical patent/EP0766788A1/fr
Application granted granted Critical
Publication of EP0766788B1 publication Critical patent/EP0766788B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/06—Control
    • F04B1/07—Control by varying the relative eccentricity between two members, e.g. a cam and a drive shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/128—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the cylinders, e.g. by moving a cylinder block
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1213—Eccentricity of an outer annular cam

Definitions

  • the invention is based on a hydrostatic radial piston machine with an adjustable cam ring according to the preamble of claim 1.
  • Such a machine is generally known. It is used in a large number of hydraulic fields of application, since its use makes it possible to reduce the effort required for control and / or regulating valves. Main advantages in drives with such
  • radial piston machines are their low loss, as well as the quick and precise electrical controllability of the machine.
  • integrated, pressurized adjusting pistons are used in the machine housing, which act on the outer circumference of the cam ring along its direction of adjustment.
  • the eccentricity of the cam ring which is proportional to the delivery rate of the machine, can be used as a controlled variable and is detected by an inductive displacement sensor. This actual value is compared with a command value by an electronic control amplifier and is used to control the position of the cam ring.
  • this inductive displacement sensor cannot be arranged in any other way than in the extension of the adjusting pistons, as a result of which the machine, in its largest dimension, is further enlarged. Since the displacement sensor is an additional attachment, the construction effort of the machine also increases.
  • a hydrostatic radial piston pump with a measuring device for detecting the eccentricity of a rotatably mounted eccentric ring is known from DE 35 13 736 AI.
  • a hydraulic linkage transmits the deflection, dependent on the eccentricity of the eccentric ring, of a master tappet, which is supported on the inside of the eccentric ring, to a slave tappet.
  • This measuring device has a large number of mechanical components and requires a high outlay for the hydraulic coupling; the signal must be picked up in a rotating machine shaft.
  • the inventive, electro-hydraulically adjustable machine with the characterizing features of the main claim has the advantage that the means used consist of inexpensive measuring devices that are integrated into existing machine components or that existing machine components are used as sensors. As a result, neither the construction volume nor the construction effort of the machine increases.
  • a digital measurement signal is present, which is provided by an electronic circuit both for determining the eccentricity of the cam ring and for determining the speed of the rotor and possibly for others
  • the scanning time is flexible within certain limits, depending on the requirements of the application, in that the number of sliding shoes used as a measuring sensor can be varied. The smallest Sampling times can therefore be achieved if all sliding blocks are used as sensors. It is also advantageous that the measuring device works without contact and is therefore not subject to friction or wear, which is evident in a long service life with little maintenance.
  • FIG. 1 shows a radial piston machine in cross section, in a simplified representation
  • FIG. 2 shows a diagram with the course of the signal generated in the transducer as a function of the time or the angle of rotation of the rotor.
  • Fig.l shows a radial piston machine 10 whose housing 11 is closed by a cover, not shown.
  • a control pin 13 which is mounted in a stationary manner in the housing, projects centrally.
  • a rotor 14 is rotatably mounted on this part of the control pin, in which a plurality of radially running bores 15 form cylinders in which working pistons 16 slide.
  • These working pistons 16 are connected in an articulated manner to sliding shoes 17 which protrude from the bores 15 of the rotor and which are movably tied to a cylindrical cam ring 18 by means of retaining rings (not shown).
  • the inside of the cam ring forms the running surface for these sliding shoes 17.
  • the cam ring is from two hydraulic adjusting pistons 22 and 23 arranged in the housing, which are diametrically opposed and form an adjusting device, are fixed in their position.
  • the position of the cam ring 18 is within the recess, along that specified by the adjusting pistons 22 and 23
  • Rotated in Fig.l not recognizable control slots are connected via longitudinal channels 26 and openings also mounted in the control pin 13 with radially extending in the housing, penetrating to the outside channels. These channels 26 represent suction and pressure channels and lead the hydraulic medium into the machine 10 and out again under pressure.
  • the angular position of the rotor 14 on the control pin 13 is designed such that the webs located between the control slots in the control pin 13 lie in an area in which the working pistons 16 are at their dead centers.
  • the rotor 14 is set in rotation by a coupling shaft, also not shown, by a drive shaft mounted in the cover.
  • the radial piston machine 10 has a measuring device for detecting the eccentricity 20 of the cam ring 18 serving as the adjusting member, which has a transducer 27 in the cam ring 18 and a plurality of transducers.
  • the sliding shoes 17 of the working pistons 16 serve as measuring sensors. The signal triggered by them in the measuring sensor is fed to an electronic evaluation unit 28.
  • the mode of operation of the adjustable radial piston machine 10 is explained in the following, its basic function in connection with the hydraulic adjusting device being assumed to be known per se.
  • the stroke ring 18 is maximally extended to the left via the adjusting device, which results in an eccentricity 20 between the stroke ring 18 and the rotor 14.
  • the above-mentioned attachment of the sliding shoes to the lifting ring 18, in connection with its eccentric position relative to the rotor 14, forces the working piston 16, which is articulated via the sliding shoes 17, in the rotor 14 upon its rotating movement to force a lifting movement in the radial direction.
  • this lifting movement in conjunction with the kinematic conditions in the radial piston machine 10, the distance between two successive sliding shoes changes.
  • this emits a voltage as a signal as long as a slide shoe 17 is above it.
  • the sensor 27 For example, if the front edge 17.1 of the sliding block 17 in the direction of rotation reaches the sensor 27, this leads in the signal curve 30 to a voltage rise 32 to a higher level 33, which is maintained until the rear edge 17.2 of the sliding block 17 slides past the sensor 27 in the direction of rotation is.
  • the voltage signal then returns to the original level 34, as a result of which a falling edge 35 is formed in the signal curve 30.
  • the voltage signal remains at this lower level 34, after which a voltage rise 32 takes place again, etc.
  • the time delay 36 between the rising and falling voltage edges, which follow one another in the signal curve, is a direct measure of the distance between the associated sliding shoes, which, as already mentioned, is proportional to the eccentricity of the cam ring 18.
  • the signal curve 30 or 31 is then processed further in the form of evaluation electronics 28 such that a falling edge 35 in the signal curve starts a counter with a high-frequency counting sequence. This counter is stopped by a rising edge 32, the counting frequency being tuned once so that the counting result corresponds to the present eccentricity 20.
  • the eccentricity 20 of the cam ring 18 can thus be determined continuously over the entire adjustment range of the cam ring 18.
  • the evaluation electronics 28 record the time 42 between two rising voltage edges 32, which is inversely proportional to the machine speed.
  • the volume flow of the machine can be recorded using both measured variables, speed and eccentricity.
  • the possible sampling interval between two signals depends both on the rotor speed and on the number of slide shoes 17 of the machine used as a measuring value transmitter.
  • Working pistons with sliding shoes can, for example, display a sampling interval of approx. 5.7 ms, which is sufficient for most applications.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Measurement Of Length, Angles, Or The Like Using Electric Or Magnetic Means (AREA)
  • Hydraulic Motors (AREA)

Abstract

L'invention a pour objet un moteur à pistons radiaux hydrostatique (10), dont la couronne réglable (18) présente des moyens incorporés servant à déterminer l'excentricité (20) entre la couronne (18) et le rotor (14). La position excentrique de la couronne (18) provoque, en liaison avec le rotor (14) entraîné en rotation et le maintien du patin de guidage (17) sur cette couronne (18), un déplacement du piston moteur (16) dans le sens radial. Cela entraîne, conjointement avec les conditions cinématiques dans le moteur à pistons radiaux (10), une modification de la distance entre deux patins successifs (17). Cette modification de la distance est proportionnelle à l'excentricité (20) de la couronne (18) et est en conséquence déterminée par un dispositif de mesure. Celui-ci présente à cet effet un transducteur (27) incorporé à la couronne (18), générant un signal de tension amplifié tant que les patins de guidage (17), agissant comme émetteurs de signaux, se déplacent au-dessus de ce transducteur. Ce signal est transmis à un dispositif électronique d'évaluation (28), où il est utilisé pour déterminer l'excentricité, la vitesse de rotation du rotor et d'autres paramètres.
EP96902897A 1995-04-13 1996-02-24 Moteur a pistons radiaux hydrostatique reglable Expired - Lifetime EP0766788B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19513987 1995-04-13
DE19513987A DE19513987C2 (de) 1995-04-13 1995-04-13 Verstellbare, hydrostatische Radialkolbenmaschine
PCT/DE1996/000313 WO1996032589A1 (fr) 1995-04-13 1996-02-24 Moteur a pistons radiaux hydrostatique reglable

Publications (2)

Publication Number Publication Date
EP0766788A1 true EP0766788A1 (fr) 1997-04-09
EP0766788B1 EP0766788B1 (fr) 2001-01-10

Family

ID=7759614

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96902897A Expired - Lifetime EP0766788B1 (fr) 1995-04-13 1996-02-24 Moteur a pistons radiaux hydrostatique reglable

Country Status (7)

Country Link
US (1) US5752427A (fr)
EP (1) EP0766788B1 (fr)
JP (1) JP3921240B2 (fr)
KR (1) KR100383156B1 (fr)
CN (1) CN1079910C (fr)
DE (2) DE19513987C2 (fr)
WO (1) WO1996032589A1 (fr)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996021107A1 (fr) * 1995-01-05 1996-07-11 Linear Anstalt Pompe permettant de refouler un milieu
DE19504220A1 (de) * 1995-02-09 1996-08-14 Bosch Gmbh Robert Verstellbare hydrostatische Pumpe
JP2921788B2 (ja) * 1996-10-16 1999-07-19 廣瀬バルブ工業株式会社 回転型液圧トランス
US5865087A (en) * 1996-10-18 1999-02-02 Olson; Howard A. Rotary variable displacement fluid power device
WO1999017021A1 (fr) * 1997-09-29 1999-04-08 S.A.I. Societa' Apparecchiature Idrauliche S.P.A. Machine hydraulique a pistons radiaux et a cylindree variable
DE10104851A1 (de) * 2001-02-03 2002-08-22 Zf Lenksysteme Gmbh Pumpsystem mit einer hydraulischen Pumpe, insbesondere für ein Lenksystem
US6916158B2 (en) 2003-04-30 2005-07-12 Actuant Corporation Radial piston pump
US7484939B2 (en) * 2004-12-17 2009-02-03 Eaton Corporation Variable displacement radial piston pump
FR2929347A1 (fr) * 2008-03-26 2009-10-02 Bia Soc Par Actions Simplifiee Convertisseur d'energie mecanique en energie hydraulique et robot mettant en oeuvre le convertisseur
DE102009054876A1 (de) * 2009-12-17 2011-06-22 ZF Friedrichshafen AG, 88046 Verfahren zur Bestimmung des Schluckvolumens einer Radialkolbenmaschine
US8907539B2 (en) * 2011-08-26 2014-12-09 General Electric Company Retaining ring configuration system
DE102014108945A1 (de) * 2014-06-26 2015-12-31 Robert Bosch Automotive Steering Gmbh Hydraulische Verstellpumpe, insbesondere für ein Lenksystem eines Kraftfahrzeuges
US10030961B2 (en) 2015-11-27 2018-07-24 General Electric Company Gap measuring device
CN109958595B (zh) * 2019-04-04 2024-04-05 山西平阳重工机械有限责任公司 手动调节式轴配流径向柱塞泵
CN110630461B (zh) * 2019-09-24 2021-02-05 浙江瑞程石化技术有限公司 一种变量径向柱塞泵
CN110617214B (zh) * 2019-10-03 2021-02-19 浙江青霄科技股份有限公司 一种双芯并联泵的泵液输送方法
WO2021207638A1 (fr) * 2020-04-10 2021-10-14 Moog Inc. Système de pompe à piston électrohydraulique à couple d'assistance
DE102022128195A1 (de) 2022-10-25 2024-04-25 Voith Patent Gmbh Hydraulische Radialkolbenmaschine

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2454732A1 (de) * 1973-06-22 1976-05-20 Bosch Gmbh Robert Regeleinrichtung fuer hydropumpen
DE3048789A1 (de) * 1980-12-23 1982-07-15 Robert Bosch Gmbh, 7000 Stuttgart Hydrostatische verdraengermaschine
DE3413913A1 (de) * 1984-04-13 1985-10-24 J.M. Voith Gmbh, 7920 Heidenheim Verstelleinrichtung fuer das verdraengungsvolumen einer verdraengermaschine
DE3420519A1 (de) * 1984-06-01 1985-12-05 Robert Bosch Gmbh, 7000 Stuttgart Hydrostatischer antrieb
JPS6131675A (ja) * 1984-07-24 1986-02-14 Nippon Denso Co Ltd 可変容量ポンプ
DE3429542A1 (de) * 1984-08-10 1986-02-20 Robert Bosch Gmbh, 7000 Stuttgart Verstellbare hydrostatische pumpe
US4711616A (en) * 1984-12-13 1987-12-08 Nippondenso Co., Ltd. Control apparatus for a variable displacement pump
DE3513736A1 (de) * 1985-04-17 1986-10-30 G. Düsterloh GmbH, 4322 Sprockhövel Hydrostatische radialkolbenmaschine
DE9104126U1 (de) * 1991-04-05 1992-08-06 Robert Bosch Gmbh, 7000 Stuttgart Radialkolbenpumpe
DE4143152C2 (de) * 1991-12-28 2001-08-23 Bosch Gmbh Robert Radialkolbenmaschine
DE4302610C2 (de) * 1993-01-30 1996-08-08 Daimler Benz Ag Verfahren zum Regeln der Pumpleistung von Schmiermittelpumpen und Schmiermittelpumpe hierfür

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9632589A1 *

Also Published As

Publication number Publication date
US5752427A (en) 1998-05-19
KR100383156B1 (ko) 2003-08-27
DE19513987C2 (de) 1998-10-08
DE59606298D1 (de) 2001-02-15
DE19513987A1 (de) 1996-10-17
EP0766788B1 (fr) 2001-01-10
JPH10501601A (ja) 1998-02-10
CN1145658A (zh) 1997-03-19
CN1079910C (zh) 2002-02-27
JP3921240B2 (ja) 2007-05-30
WO1996032589A1 (fr) 1996-10-17

Similar Documents

Publication Publication Date Title
EP0766788B1 (fr) Moteur a pistons radiaux hydrostatique reglable
DE3239266C2 (fr)
DE2330607A1 (de) Taumelscheibenpumpe mit veraenderbarem hubvolumen
DE19504220A1 (de) Verstellbare hydrostatische Pumpe
WO2007068447A1 (fr) Dispositif et procede d'entretien d'unites de refoulement hydrostatique en fonction de leur etat
DE3208250A1 (de) Einrichtung zum steuern und/oder regeln einer axialkolbenmaschine
DE19513767B4 (de) Verstellbare, hydrostatische Radialkolbenmaschine
DE202007007144U1 (de) Exzenterpresse
DE19601749A1 (de) Betätigungseinrichtung, vorzugsweise für Fahrzeuge, insbesondere für Kraftfahrzeuge
EP1086802B1 (fr) Presse avec entraînement à vilebrequin pour le poinçon supérieur et son procédé de fonctionnement
EP0953767B1 (fr) Machine hydrostatique
EP3728761B1 (fr) Manipulateur avec mecanisme d'entrainement en rotation
EP0471695B1 (fr) Entrainement hydraulique
DE4021557C2 (de) Vorrichtung zur Überwachung des Durchflusses eines fließfähigen Mediums durch einen Strömungsraum
DE102018218548A1 (de) Hydrostatische Kolbenmaschine
EP1283365B1 (fr) Moteur hydraulique avec frein intégré
DE3813081A1 (de) Kollerpresse mit einer hydraulikeinrichtung
EP0383167A1 (fr) Moteur à pistons axiaux
DE102004028396A1 (de) Bodenkopiervorrichtung
DE10121383C2 (de) Steuerung für eine Unwucht-Verstelleinrichtung in einem Vibrationserreger einer Bodenverdichtungsvorrichtung
DE3227526C2 (fr)
EP1176314B1 (fr) Procédé et dispositif pour compenser la compressibilité dans des commandes hydrauliques
DE202007019293U1 (de) Schwingungserreger für Bodenverdichtungsvorrichtungen
WO1997018394A1 (fr) Dispositif a au moins deux cylindres d'entrainement
DE102006005356A1 (de) Hydraulischer Linearmotor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17P Request for examination filed

Effective date: 19970417

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

17Q First examination report despatched

Effective date: 20000316

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT

ET Fr: translation filed
REF Corresponds to:

Ref document number: 59606298

Country of ref document: DE

Date of ref document: 20010215

ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN P. & C. S.N.C.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20010320

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

26N No opposition filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

REG Reference to a national code

Ref legal event code: R082

Ref document number: 59606298

Representative=s name: FLEUCHAUS & GALLO PARTNERSCHAFT MBB, DE

Ref country code: DE

Country of ref document: DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 59606298

Country of ref document: DE

Representative=s name: JOSTARNDT PATENTANWALTS-AG, DE

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20140220

Year of fee payment: 19

Ref country code: FR

Payment date: 20140226

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20140228

Year of fee payment: 19

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20140430

Year of fee payment: 19

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 59606298

Country of ref document: DE

Representative=s name: FLEUCHAUS & GALLO PARTNERSCHAFT MBB, DE

Ref country code: DE

Ref legal event code: R082

Ref document number: 59606298

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59606298

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20150224

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20151030

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150224

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150224

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150901

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150302